WO2019167135A1

WO2019167135A1 - Device and method for controlling valve timing adjustment device

Info

Publication number: WO2019167135A1
Application number: PCT/JP2018/007310
Authority: WO
Inventors: 拓也近山; 横山　雅之
Original assignee: 三菱電機株式会社
Priority date: 2018-02-27
Filing date: 2018-02-27
Publication date: 2019-09-06
Also published as: US10989079B2; US20200271021A1; DE112018006580T5; JPWO2019167135A1; DE112018006580B4; JP6683409B2

Abstract

In the present invention, an ECU (101) supplies lock pin-releasing hydraulic pressure to an advance-angle lock pin-releasing oil passage (5a) to release engagement of an advance-angle lock pin (6) from an advance-angle engagement groove (9), places a rotor (1) in a state of being able to rotate to an advance-angle side, and creates a gap between the advance-angle engagement groove (9) and the advance-angle lock pin (6), for establishing communication to a delay-angle lock pin-releasing oil passage (5c). Next, the ECU (101) supplies hydraulic pressure to an advance-angle hydraulic chamber (16) to cause the rotor (1) to rotate, and supplies lock pin-releasing hydraulic pressure to a delay-angle engagement groove (10) by way of the gap and the delay-angle lock pin-releasing oil passage (5c) to release engagement of a delay-angle lock pin (7).

Description

Control device and control method for valve timing adjusting device

The present invention relates to a control device and a control method for a valve timing adjusting device for engaging a lock pin at an intermediate position set between a most advanced angle position and a most retarded angle position.

Conventionally, a valve timing adjusting device for controlling the opening / closing timing of the intake or exhaust valve has been devised. The valve timing adjusting device includes a first rotating body, a second rotating body capable of rotating at a predetermined angle relative to the first rotating body, and a lock mechanism for locking the second rotating body at an intermediate position when the engine is started. It has.

For example, a control device for a valve timing adjusting device according to Patent Document 1 supplies hydraulic pressure to an advance hydraulic chamber and applies an advance side rotational force to a second rotating body to attach an advance lock pin to an advance engagement hole. In this state, the hydraulic pressure is supplied to the advance angle engagement hole and the retard angle engagement hole to release the engagement of the delay angle lock pin from the delay angle engagement groove. Thereafter, the control device supplies hydraulic pressure to the retard hydraulic chamber to apply a retard rotational force to the second rotating body, and releases the advance lock pin away from the peripheral surface of the advance engagement hole. It was necessary to follow the procedure.

International Publication No. 2015/033676

The control device of the valve timing adjusting device according to Patent Document 1 needs to supply advance hydraulic pressure, lock pin release hydraulic pressure, and retard hydraulic pressure in order to release the intermediate lock. Therefore, it takes a long time to release the intermediate lock and operate the valve timing adjusting device, and there is a problem that the responsiveness is poor.

The present invention has been made to solve the above-described problems, and it is an object of the present invention to shorten the time required to release the intermediate lock and operate the valve timing adjusting device and improve the responsiveness. .

A control device for a valve timing adjusting device according to the present invention has a first rotating body having a working hydraulic chamber, and a vane that is housed in the first rotating body and divides the working hydraulic chamber into an advance side and a retard side. A second rotating body that rotates relative to the first rotating body, and a lock mechanism that locks the second rotating body at an intermediate position between the most advanced angle position and the most retarded angle position. A through hole formed in the vane in the axial direction of the second rotating body, and a cylindrical cylindrical member incorporated in the through hole in a state in which axial sliding and radial rotation with the through hole are restricted A first lock pin and a second lock pin that are coaxially disposed inside the cylindrical member, a first engagement groove formed on the first rotating body and engaged with the first lock pin and the second lock pin, and The second engagement groove and the first lock pin are urged in the direction of the first engagement groove to move the second lock pin. And a first lock pin that is formed on the outer peripheral surface of the cylindrical member or the inner peripheral surface of the through hole and supplies lock pin release hydraulic pressure to the first engagement groove. A release oil passage and a second lock pin release oil passage that is formed on the outer peripheral surface of the cylindrical member or the inner peripheral surface of the through hole and supplies the lock pin release oil pressure supplied to the first engagement groove to the second engagement groove. The first lock pin is engaged with the first engagement groove, the second lock pin is engaged with the second engagement groove, and the second rotating body is moved to the intermediate position. In the locked state, the lock pin releasing oil pressure is supplied to the first lock pin releasing oil passage to disengage the first lock pin from the first engaging groove, and the second rotating body is advanced or retarded. To the second lock pin releasing oil passage between the first engagement groove and the first lock pin. A hydraulic pressure is supplied to the working hydraulic chamber on the side where the second rotating body is allowed to rotate to rotate the second rotating body, and the lock pin release hydraulic pressure of the first engagement groove is changed to the clearance and the second rotating body. The second lock pin is supplied to the second engaging groove via the lock pin releasing oil passage to disengage the second lock pin to release the lock of the second rotating body.

According to the present invention, since the intermediate lock is released by supplying the lock pin releasing hydraulic pressure and either the advance angle or the retarded oil pressure, the intermediate lock is released and the valve is released as compared with the conventional case. The time required for operating the timing adjustment device can be shortened, and the responsiveness can be improved.

1 is an exploded perspective view showing a configuration example of a valve timing adjustment device according to Embodiment 1. FIG. 1 is an exploded perspective view showing a configuration example of a valve timing adjustment device according to Embodiment 1. FIG. 1 is a front view illustrating a configuration example of a valve timing adjustment device according to a first embodiment. It is a figure which shows the structural example of the press-fit member of Embodiment 1, FIG. 4A shows the end surface by the side of a plate, FIG. 4B shows a cross section, FIG. 4C shows the end surface by the side of a cover. FIG. 4 is a cross-sectional view of the locking mechanism of the first embodiment taken along line PP in FIG. 3 and shows a locked state. FIG. 4 is a cross-sectional view of the lock mechanism of the first embodiment cut along the line PP in FIG. 3 and shows a lock release state. FIG. 6 is a front view showing a shape example of an advance angle engagement groove and a retard angle engagement groove according to the first embodiment. FIG. 4 is a cross-sectional view of the lock mechanism of the second embodiment taken along the line PP in FIG. 3 and shows a locked state. FIG. 10 is a front view showing a shape example of an advance angle engagement groove and a retard angle engagement groove according to the second embodiment. FIG. 10 is a cross-sectional view of the locking mechanism of the third embodiment taken along the line PP in FIG. 3, showing a locked state. FIG. 10 is a cross-sectional view of the lock mechanism of the fourth embodiment, taken along line QQ in FIG. 3, and shows a locked state. FIG. 10 is a front view showing a shape example of an advance angle engagement groove and a retard angle engagement groove of a fourth embodiment. FIG. 10 is a diagram illustrating a configuration example related to operation control of a valve timing adjustment device according to a fifth embodiment. 14A and 14B are views showing a state in which the valve timing adjusting device is locked at an intermediate position. FIG. 14A is a cross-sectional view taken along line QQ in FIG. 3, and FIG. 14B is along line PP in FIG. It is sectional drawing cut | disconnected. FIG. 15A is a view showing a state where the advance lock pin is disengaged and the retard lock pin release oil passage is opened, FIG. 15A is a cross-sectional view taken along the line QQ of FIG. 3, and FIG. It is sectional drawing cut | disconnected along the PP line | wire. FIG. 16A is a cross-sectional view taken along the line QQ of FIG. 3 and FIG. 16B is a cross-sectional view of FIG. It is sectional drawing cut | disconnected along the P line. FIGS. 17A and 17B are views showing a state in which the rotor is operated to the retard side upon receiving the retard oil pressure, FIG. 17A is a cross-sectional view taken along the line QQ in FIG. 3, and FIG. It is sectional drawing cut | disconnected along. 10 is a flowchart showing a lock release procedure of the valve timing adjustment device according to the fifth embodiment. 10 is a graph showing a phase control duty, an actual phase, a release oil passage supply / discharge state, an advance angle lock pin engagement state, and a retard angle lock pin engagement state when lock release is performed in the fifth embodiment. FIG. 4 is a view showing a state in which the rotor is on the advance side, and is a cross-sectional view taken along the line QQ in FIG. 3. FIG. 4 is a view showing a state in which a retard lock pin is engaged with a step portion of a retard engagement groove, and is a cross-sectional view taken along the line QQ in FIG. 3. FIG. 4 is a view showing a state in which the valve timing adjusting device is locked at an intermediate position, and is a cross-sectional view taken along the line QQ in FIG. 3. 10 is a flowchart illustrating a locking procedure of the valve timing adjustment device according to the fifth embodiment. 16 is a graph showing a phase control duty, an actual phase, a release oil passage supply / discharge state, an advance lock pin engagement state, and a retard lock pin engagement state at the time of locking in the fifth embodiment. FIG. 10 is an exploded perspective view illustrating a configuration example of a rotor and a press-fitting member in a valve timing adjustment device according to a sixth embodiment. FIG. 10 is a cross-sectional view of the lock mechanism of the sixth embodiment, taken along line PP in FIG. 3, showing a locked state.

Hereinafter, in order to explain the present invention in more detail, modes for carrying out the present invention will be described with reference to the accompanying drawings.
Embodiment 1 FIG.
FIG. 1 is an exploded perspective view showing a configuration example of a valve timing adjusting apparatus 100 according to Embodiment 1, as viewed from the front side. FIG. 2 is an exploded perspective view showing a configuration example of the valve timing adjusting apparatus 100 according to Embodiment 1, as viewed from the back side. In FIG. 1 and FIG. 2, the coil spring 8 is not shown. FIG. 3 is a front view showing a configuration example of the valve timing adjusting device 100 according to the first embodiment, and shows a locked state in which the case 2 is locked at an intermediate position. In FIG. 3, the illustration of the plate 3 is omitted.

The case 2 has a plurality of shoes 11 that project to the inner periphery and form a plurality of working hydraulic chambers. The rotor 1 has a plurality of vanes 12 that divide the working hydraulic chamber of the case 2 into an advance hydraulic chamber 16 and a retard hydraulic chamber 17. In a state where the rotor 1 is accommodated in the case 2, the plate 3, the case 2, and the cover 4 are integrated by screws or the like. Due to the integration, both sides of the case 2 are closed by the plate 3 and the cover 4, and the working hydraulic chamber is sealed. The case 2, the plate 3 and the cover 4 constitute a first rotating body. The second rotating body is constituted by the rotor 1. The second rotator is rotatable relative to the first rotator.

The sprocket 2a is formed on the outer periphery of the case 2. The driving force of the engine crankshaft is transmitted to the case 2 by a timing belt (not shown) attached to the sprocket 2a, and the first rotating body constituted by the case 2, the plate 3 and the cover 4 rotates synchronously with the crankshaft. To do. On the other hand, the rotor 1 is fixed to a camshaft 20 shown in FIG. 5, which will be described later, and rotates synchronously with the camshaft.

In the rotor 1, a plurality of advance oil passages 18, a plurality of retard oil passages 19, and one rotor-side lock pin release oil passage 14 are formed. Each advance oil passage 18 communicates with each advance hydraulic chamber 16, and each retard oil passage 19 communicates with each retard hydraulic chamber 17. The rotor side lock pin release oil passage 14 communicates with an advance lock pin release oil passage 5a described later.

The oil pressure supplied and discharged from an oil control valve 102 (hereinafter referred to as “OCV 102”) shown in FIG. 13 to be described later is passed through an advance oil passage 18 and a retard oil passage 19, and the advance oil chamber 16 and It is supplied to and discharged from the retarded hydraulic chamber 17. By supplying hydraulic pressure to the advance hydraulic chamber 16, when the relative phase of the second rotary body with respect to the first rotary body is adjusted to the advance side, the relative phase of the camshaft with respect to the crankshaft changes to the advance side. Accordingly, the opening / closing timing of the intake valve or exhaust valve of the engine also changes. On the other hand, when the relative phase of the second rotating body with respect to the first rotating body is adjusted to the retarding side by supplying hydraulic pressure to the retarding hydraulic chamber 17, the relative phase of the camshaft with respect to the crankshaft is retarded. The opening / closing timing of the intake valve or exhaust valve of the engine also changes. In FIG. 3, the direction in which the rotor 1 rotates clockwise with respect to the case 2 is the advance side, and the direction in which the rotor 1 rotates counterclockwise is the retard side.

Also, the vane 12 of the rotor 1 is provided with a lock mechanism for locking the rotor 1 at an intermediate position between the most advanced position and the most retarded position. The intermediate position may be any position between the most advanced position and the most retarded position, and does not need to be strictly an intermediate position. The details of the locking mechanism will be described below with reference to FIGS.

FIG. 4 is a diagram showing a configuration example of the press-fitting member 5, FIG. 4A shows an end face on the plate 3 side, FIG. 4B shows a cross section, and FIG. 4C shows an end face on the cover 4 side. FIG. 5 is a cross-sectional view of the locking mechanism of the first embodiment taken along the line PP in FIG. 3, and shows a locked state. 6 is a cross-sectional view of the locking mechanism of the first embodiment taken along the line PP in FIG. 3, and shows the unlocked state. FIG. 7 is a front view showing a shape example of the advance engagement groove 9 and the retard engagement groove 10 of the first embodiment. In FIG. 7, the outer shape of the advance angle engaging groove 9 is shown by a solid line, the outer shape of the retard angle engaging groove 10 is shown by a broken line, and the outer shapes of the advance angle lock pin 6 and the retard angle lock pin 7 are two-dot chain lines. Indicated.

A through hole 13 is formed in the vane 12 so as to penetrate the vane 12 in the axial direction of the case 2. A cylindrical press-fitting member 5 is press-fitted into the through hole 13. The press-fitting member 5 is incorporated into the through-hole 13 in a state where axial sliding and radial rotation with the through-hole 13 are restricted by being press-fitted into the through-hole 13. The press-fitting member 5 only needs to be connected to the rotor-side lock pin release oil passage 14 of the rotor 1 to form a lock pin release oil passage, as will be described later. There is no. For example, even if the cylindrical member is inserted into the through-hole 13, if the cylindrical member does not slide in the axial direction and does not rotate in the radial direction, the same function as the press-fitting member 5 can be achieved. it can.

In the press-fitting member 5, an advance lock pin 6 and a retard lock pin 7 are arranged coaxially. An arc-shaped groove along the radius of curvature of the rotation direction of the case 2 is formed at a position facing the advance lock pin 6 on the plate 3, and a notch 5 b of a press-fitting member 5 described later faces the arc-shaped groove from the arc-shaped groove. Grooves projecting in the direction to be formed are also formed, and the advance engagement grooves 9 are constituted by these grooves. Further, an arc-shaped groove along the radius of curvature of the case 2 in the rotational direction of the case 2 is formed in the cover 4 at a position facing the retard lock pin 7, and a notch 5c2 of a press-fitting member 5 described later is formed from the arc-shaped groove. Grooves projecting in the direction facing each other are also formed, and the retard engagement grooves 10 are constituted by these grooves.

One coil spring 8 as an urging member is disposed between the advance lock pin 6 and the retard lock pin 7. The coil spring 8 urges the advance lock pin 6 in the direction of the advance engagement groove 9 to engage the advance lock pin 6 with the advance engagement groove 9 and also retards the retard lock pin 7. The retard lock pin 7 is engaged with the retard engagement groove 10 by urging in the direction of the corner engagement groove 10.

A groove extending from the rotor-side lock pin release oil passage 14 to the advance engagement groove 9 is formed on the outer peripheral surface of the press-fitting member 5, and this groove serves as an advance lock pin release oil passage 5a. This groove is closed and sealed by the inner peripheral surface of the through-hole 13 and the inner surface of the plate 3. Further, the press-fitting member 5 is notched at a portion facing the advance angle engaging groove 9 in the advance angle lock pin releasing oil passage 5a to form a notch portion 5b. Due to the presence of the notch 5b, the advance lock pin releasing oil passage 5a and the advance engagement groove 9 communicate with each other. The lock pin releasing oil pressure supplied to the rotor side lock pin releasing oil passage 14 is transferred from the rotor side lock pin releasing oil passage 14 to the advance angle engaging groove 9 via the advance angle lock pin releasing oil passage 5a and the notch portion 5b. Supplied with. The lock pin releasing hydraulic pressure supplied to the advance angle engaging groove 9 causes the advance angle lock pin 6 to retreat from the advance angle engaging groove 9 against the urging force of the coil spring 8, and the advance angle lock pin 6 and the advance angle are advanced. The engagement with the engagement groove 9 is released. When engaged, the oil stored in the advance angle engaging groove 9 is discharged to the rotor side lock pin releasing oil passage 14 via the advance angle lock pin releasing oil passage 5a.

Further, on the outer peripheral surface of the press-fitting member 5, a groove extending from the advance engagement groove 9 to the retard engagement groove 10 and notches 5c1 and 5c2 in which both ends of the groove are notched are formed. These grooves and the notches 5c1 and 5c2 form a retard lock pin releasing oil passage 5c. These grooves and the notches 5c1 and 5c2 are closed and sealed by the inner peripheral surface of the through hole 13, the inner surface of the plate 3, and the inner surface of the cover 4. However, when the advance lock pin 6 is retracted from the advance engagement groove 9 and the engagement is released, a gap is generated between the advance lock pin 6 and the advance engagement groove 9, and this clearance is The retard lock pin release oil passage 5c communicates with the notch 5c1 on the advance engagement groove 9 side. Further, the notch 5 c 2 is formed at a position facing the retarding engagement groove 10. The lock pin releasing hydraulic pressure supplied to the advance angle engaging groove 9 is delayed from the clearance generated between the advance angle lock pin 6 and the advance angle engaging groove 9 via the retard angle lock pin releasing oil passage 5c. It is supplied to the corner engaging groove 10. The lock pin releasing hydraulic pressure supplied to the retard engagement groove 10 causes the retard lock pin 7 to retreat from the retard engagement groove 10 against the urging force of the coil spring 8, so that the retard lock pin 7 and the retard angle are retarded. The engagement with the engagement groove 10 is released. When engaged, the oil stored in the retard engagement groove 10 is released through the retard lock pin release oil passage 5c, the advance engagement groove 9, and the advance lock pin release oil passage 5a. It is discharged to the oil passage 14.

The groove of the advance lock pin release oil passage 5a or the groove of the retard lock pin release oil passage 5c may have a linear shape or an arbitrary shape such as a spiral shape.
In the illustrated example, the advance angle lock pin release oil passage 5a and the retard angle lock pin release oil passage 5c are arranged at equal intervals, but the positional relationship between the both oil passages may be arbitrary.

As shown in FIG. 5, the biasing force of the coil spring 8 acts to engage the advance lock pin 6 with the advance engagement groove 9, and the retard lock pin 7 with the retard engagement groove 10. In a state where the rotor 1 is engaged with the rotor 1, the rotor 1 is locked at the intermediate position. On the other hand, as shown in FIG. 6, the lock pin release hydraulic pressure supplied from the rotor side lock pin release oil passage 14 acts to disengage the advance lock pin 6 from the advance engagement groove 9, and In a state where the retard lock pin 7 is disengaged from the retard engagement groove 10, the rotor 1 can be relatively rotated. The advance lock pin 6 and the retard lock pin 7 retracted from the advance engagement groove 9 and the retard engagement groove 10 come into contact with the stopper 5f of the press-fitting member 5, thereby causing the advance lock pin 6 and the retard angle. Further retreat of the lock pin 7 is restricted.

Since the advance lock pin 6 does not receive the cam torque in the retard direction, it is easy to come out from the advance engagement groove 9. On the other hand, since the retard lock pin 7 receives the cam torque and is pressed against the retard side wall of the retard engagement groove 10, it is difficult to come out of the retard engagement groove 10. Therefore, the lock mechanism of the first embodiment is configured to first disengage the advance lock pin 6 that does not receive cam torque, and then to disengage the retard lock pin 7. With this configuration, the advance lock pin 6 can be reliably disengaged prior to the retard lock pin 7.

In order to reliably release the advance lock pin 6 prior to the retard lock pin 7, it is desirable to adopt the configuration described below.
The length of the notch 5b in the axial direction of the case 2 is “A”. The length of the gap between the advance lock pin 6 and the advance engagement groove 9 in the axial direction of the case 2 is “B”. The gap “B” is a gap that is generated when the advance lock pin 6 is disengaged from the advance engagement groove 9, and the lock pin from the advance engagement groove 9 to the retard lock pin release oil passage 5c. The oil passage is supplied with the release hydraulic pressure. The magnitude relationship between A and B is A> B in the locked state shown in FIG. 5, and A ≦ B in the unlocked state shown in FIG. Because of this magnitude relationship, the retard lock pin release oil passage 5c is not secured unless the advance lock pin 6 is disengaged in the locked state of FIG. 5, and therefore the advance lock pin 6 is securely engaged. Can be canceled.

At the position of the stopper 5 f of the press-fitting member 5, a fluid drainage path 5 d that is a through hole that communicates the inside and outside of the press-fitting member 5 is formed. In addition, on the outer peripheral surface of the press-fitting member 5, a fluid drain passage 5 e that is a groove that communicates the fluid drain passage 5 d and the rotor-side fluid drain passage 15 is formed. There are always gaps between the press-fitting member 5 and the advance lock pin 6 and between the press-fit member 5 and the retard lock pin 7 for sliding the advance lock pin 6 and the retard lock pin 7. . Oil and air enter the inside of the press-fitting member 5 through this gap. The oil and air are discharged from the rotor-side fluid drainage path 15 to the outside via the fluid drainage path 5d and the fluid drainage path 5e.

As described above, the through hole 13 constituting the locking mechanism of the first embodiment is formed inside the vane 12 in the axial direction of the case 2 that is the second rotating body. The press-fitting member 5 is a cylindrical member, and is incorporated into the through-hole 13 in a state in which axial sliding and radial rotation with the through-hole 13 are restricted. The advance lock pin 6 and the retard lock pin 7 are arranged coaxially inside the press-fitting member 5. The advance angle engaging groove 9 and the retard angle engaging groove 10 are formed in the plate 3 and the cover 4 as the first rotating body, and the advance angle lock pin 6 and the retard angle lock pin 7 are engaged with each other. The coil spring 8 urges the advance lock pin 6 toward the advance engagement groove 9 and urges the retard lock pin 7 toward the retard engagement groove 10. The advance lock pin release oil passage 5 a is formed on the outer peripheral surface of the press-fitting member 5 and supplies lock pin release oil pressure to the advance engagement groove 9. The retard lock pin release oil passage 5 c is formed on the outer peripheral surface of the press-fitting member 5, and supplies the lock pin release hydraulic pressure supplied to the advance engagement groove 9 to the retard engagement groove 10. As described above, since the simple-shaped longitudinal grooves formed on the outer peripheral surface of the press-fitting member 5 are used as the advance lock pin release oil passage 5a and the retard lock pin release oil passage 5c, a complicated shape is formed inside the vane 12. It is not necessary to process the lock pin releasing oil passage, and it is only necessary to process the through hole 13 having a simple shape in the vane 12.

Further, the press-fitting member 5 of the first embodiment has a notch portion 5b in which a portion facing the advance angle engaging groove 9 in the advance angle lock pin releasing oil passage 5a is notched. In this configuration, when the advance lock pin 6 is engaged with the advance engagement groove 9, the advance lock pin 6 communicates with the advance lock pin release oil passage 5 c in the axial direction of the case 2 to advance. The length B of the gap with the corner engaging groove 9 is less than the length A of the notch 5b. On the other hand, in a state in which the advance lock pin 6 is disengaged from the advance engagement groove 9, the advance lock pin 6 communicates with the advance lock pin release oil passage 5c in the axial direction of the case 2 and the advance angle. The length B of the gap with the engagement groove 9 is equal to or longer than the length A of the notch 5b. As a result, the advance lock pin 6 can be reliably disengaged prior to the retard lock pin 7.

Further, the press-fitting member 5 according to the first embodiment has

fluid drain paths

5d and 5e for discharging the fluid between the advance lock pin 6 and the retard lock pin 7 to the outside. On the other hand, on the vane 12 side, it is only necessary to process a vertical hole communicating with the

fluid drain paths

5d, 5e, that is, the rotor side fluid drain path 15. Conventionally, a method of machining a horizontal hole in the rotor 1 to obtain a rotor-side fluid drainage path is often used. However, in the first embodiment, a vertical hole can be machined in the rotor 1 to obtain the rotor-side fluid drainage path 15. Thereby, the fluid drainage path can be realized by easier processing than in the past.
In addition, the structure which does not provide the fluid drainage path 5e but directly communicates the fluid drainage path 5d with the rotor-side fluid drainage path 15 may be used.

Further, the coil spring 8 of the first embodiment may have a linear spring constant or a non-linear spring constant. The coil spring 8 having a non-linear spring constant is an unequal pitch spring or the like whose urging force changes during expansion and contraction. For example, using the coil spring 8 having a non-linear spring constant, the retard lock pin 7 is set to the retard engagement groove 10 as compared with the force for urging the advance lock pin 6 toward the advance engagement groove 9. Increase the force to urge in the direction of. As a result, even when the lock pin releasing hydraulic pressure leaks to the retarded angle engaging groove 10 through the gap at the time of unlocking, the retarded angle lock pin 6 is released before the advanced angle lock pin 6 is disengaged from the advanced angle engaged groove 9. 7 can be prevented from being disengaged from the retarded engagement groove 10.

Embodiment 2. FIG.
Since the valve timing adjustment device 100 according to the second embodiment has the same configuration as the valve timing adjustment device 100 according to the first embodiment except for the lock mechanism, FIGS. 1 to 7 are used. FIG. 8 is a cross-sectional view of the lock mechanism of the second embodiment taken along the line PP in FIG. 3, and shows a locked state. FIG. 9 is a front view showing a shape example of the advance angle engaging groove 9 and the retard angle engaging groove 10 of the second embodiment. In FIG. 9, the outer shape of the advance angle engaging groove 9 is shown by a solid line, the outer shape of the retard angle engaging groove 10 is shown by a broken line, and the outer shapes of the advance angle lock pin 6 and the retard angle lock pin 7 are two-dot chain lines. Indicated. 8 and 9, the same or corresponding parts as those in FIGS. 1 to 7 are designated by the same reference numerals and the description thereof is omitted.

In the first embodiment, the press-fitting member 5 has the notch 5b, but in the second embodiment, a recess 9a is formed instead of the notch 5b. That is, the advance angle engaging groove 9 has a recessed portion 9a in which a portion facing the advance angle lock pin releasing oil passage 5a is recessed. Due to the presence of the recess 9a, the advance lock pin release oil passage 5a and the advance engagement groove 9 communicate with each other. The lock pin release hydraulic pressure supplied to the rotor side lock pin release oil passage 14 is transferred from the rotor side lock pin release oil passage 14 to the advance engagement groove 9 via the advance lock pin release oil passage 5a and the recess 9a. Supplied.

Note that, similarly to the advance side, the recess 10a may be formed in the retard engagement groove 10 instead of the notch 5c2 on the retard side. The lock pin releasing hydraulic pressure supplied to the advance angle engaging groove 9 is transferred from the advance angle engaging groove 9 to the retard angle engaging groove 10 via the notch 5c1, the retard angle lock pin releasing oil passage 5c, and the recess 10a. Supplied.

Here, the length of the concave portion 9a in the axial direction of the case 2 is assumed to be “A”. Similarly to the first embodiment, the length of the gap between the advance lock pin 6 and the advance engagement groove 9 in the axial direction of the case 2 is “B”. The magnitude relationship between A and B is A> B in the locked state shown in FIG. 8, and A ≦ B in the unlocked state (not shown). Because of this magnitude relationship, in the locked state of FIG. 8, unless the advance lock pin 6 is disengaged, the retard lock pin release oil passage 5c is not secured, so that the advance lock pin 6 is securely engaged. Can be canceled.

As described above, the advance angle engaging groove 9 of the second embodiment has the recessed portion 9a in which the portion facing the advance angle lock pin releasing oil passage 5a is recessed. In this configuration, when the advance lock pin 6 is engaged with the advance engagement groove 9, the advance lock pin 6 communicates with the advance lock pin release oil passage 5 c in the axial direction of the case 2 to advance. The length B of the gap with the corner engaging groove 9 is less than the length A of the recess 9a. On the other hand, in a state in which the advance lock pin 6 is disengaged from the advance engagement groove 9, the advance lock pin 6 communicates with the advance lock pin release oil passage 5c in the axial direction of the case 2 and the advance angle. The length B of the gap with the engagement groove 9 is not less than the length A of the recess 9a. As a result, the advance lock pin 6 can be reliably disengaged prior to the retard lock pin 7.

Embodiment 3 FIG.
Since the valve timing adjustment device 100 according to the third embodiment has the same configuration as the valve timing adjustment device 100 according to the first embodiment except for the lock mechanism, FIGS. 1 to 7 are used. FIG. 10 is a cross-sectional view of the locking mechanism of the third embodiment taken along the line PP in FIG. 3, and shows a locked state. 10, parts that are the same as or correspond to those in FIGS. 1 to 9 are given the same reference numerals, and descriptions thereof are omitted.

In the first embodiment, the press-fitting member 5 has the notch 5b, but in the third embodiment, the recess 9a shown in the second embodiment is formed in addition to the notch 5b. That is, the advance angle engaging groove 9 has a concave portion 9a in which a portion facing the notch portion 5b of the press-fitting member 5 is recessed. Due to the presence of the notch 5b and the recess 9a, the advance lock pin releasing oil passage 5a and the advance engagement groove 9 communicate with each other. The lock pin release hydraulic pressure supplied to the rotor side lock pin release oil passage 14 is advanced from the rotor side lock pin release oil passage 14 via the advance lock pin release oil passage 5a, the notch 5b, and the recess 9a. It is supplied to the groove 9.

It should be noted that, similarly to the advance side, a recess 10a may be formed in the retard engagement groove 10 on the retard side in addition to the notch 5c2. The lock pin release hydraulic pressure supplied to the advance engagement groove 9 is retarded via the advance engagement groove 9 via the notch 5c1, the retard lock pin release oil passage 5c, the notch 5c2, and the recess 10a. It is supplied to the groove 10.

Here, the length obtained by adding the length of the notch 5b and the length of the recess 9a in the axial direction of the case 2 is defined as “A”. Similarly to the first embodiment, the length of the gap between the advance lock pin 6 and the advance engagement groove 9 in the axial direction of the case 2 is “B”. The magnitude relationship between A and B is A> B in the locked state shown in FIG. 10, and A ≦ B in the unlocked state (not shown). Because of this magnitude relationship, in the locked state of FIG. 10, unless the advance angle lock pin 6 is disengaged, the retard angle lock pin release oil passage 5c is not secured, so the advance angle lock pin 6 is reliably engaged. Can be canceled.

As described above, the press-fitting member 5 of the third embodiment has the cutout portion 5b in which the portion facing the advance angle engagement groove 9 in the advance angle lock pin releasing oil passage 5a is notched. Further, the advance angle engaging groove 9 has a recess 9a in which a portion facing the notch 5b is recessed. In this configuration, when the advance lock pin 6 is engaged with the advance engagement groove 9, the advance lock pin 6 communicates with the advance lock pin release oil passage 5 c in the axial direction of the case 2 to advance. The length B of the gap with the corner engaging groove 9 is less than the length A obtained by adding the length of the notch 5b and the length of the recess 9a. On the other hand, in a state in which the advance lock pin 6 is disengaged from the advance engagement groove 9, the advance lock pin 6 communicates with the advance lock pin release oil passage 5c in the axial direction of the case 2 and the advance angle. The length B of the gap with the engagement groove 9 is equal to or longer than the length A obtained by adding the length of the notch 5b and the length of the recess 9a. As a result, the advance lock pin 6 can be reliably disengaged prior to the retard lock pin 7.

In the first embodiment, one coil spring 8 is used, but in the third embodiment, two

coil springs

8a and 8b are used. A coil spring 8 a corresponding to the first coil spring biases the advance lock pin 6 toward the advance engagement groove 9. A coil spring 8 b corresponding to the second coil spring biases the retard lock pin 7 toward the retard engagement groove 10. The urging force of the coil spring 8b may be made stronger than the urging force of the coil spring 8a. As a result, even when the lock pin releasing hydraulic pressure leaks to the retarded angle engaging groove 10 through the gap at the time of unlocking, the retarded angle lock pin 6 is released before the advanced angle lock pin 6 is disengaged from the advanced angle engaged groove 9. 7 can be prevented from being disengaged from the retarded engagement groove 10.

Embodiment 4 FIG.
Since the valve timing adjusting apparatus 100 according to the fourth embodiment has the same configuration as the valve timing adjusting apparatus 100 according to the first embodiment except for the lock mechanism, FIGS. 1 to 7 are used. FIG. 11 is a cross-sectional view of the locking mechanism of the fourth embodiment, taken along line QQ in FIG. 3, and shows a locked state. FIG. 12 is a front view showing an example of the shape of the advance engagement groove 9 and the retard engagement groove 10 of the fourth embodiment.

In the first embodiment, the depths of the advance angle engaging groove 9 and the retard angle engagement groove 10 are constant in the relative rotation direction, but in the fourth embodiment, the retard angle side of the advance angle engagement groove 9 is set. Are formed with at least one stepped portion 9b, and the advancement engaging groove 9 has a multi-step depth. Further, at least one stepped portion 10b is formed on the advance side of the retard engagement groove 10, and the depth of the retard engagement groove 10 is multistage. Note that the depth may be multi-stage only on the advance side or only the retard side, or the depths on both the advance side and the retard side may be multi-stage. Accordingly, even when either the advance lock pin 6 or the retard lock pin 7 is in the engaged state, even if the valve timing adjusting device 100 receives vibration, the advance lock pin 6 or the retard lock pin 7. However, it abuts against the wall constituted by the advance angle engaging groove 9 and the stepped portion 9b or the wall constituted by the retarded angle engaging groove 10 and the stepped portion 10b, and the relative rotation of the rotor 1 is prevented.

In the valve timing adjusting apparatus 100 according to the second and third embodiments, the stepped portion 9b and the stepped portion 10b may be formed in the advance angle engaging groove 9 and the retard angle engaging groove 10.

Embodiment 5 FIG.
FIG. 13 is a diagram illustrating a configuration example relating to operation control of the valve timing adjusting apparatus 100 according to the fifth embodiment. Since the valve timing adjusting device 100 according to the first embodiment has the same configuration as the valve timing adjusting device 100 according to the first to fourth embodiments, FIG. 1 to FIG. 12 are used. The valve timing adjustment system shown in FIG. 13 includes an engine control unit 101 (hereinafter referred to as “ECU 101”) that is a control device of the valve timing adjustment device 100, an OCV 102, and a valve timing adjustment device 100.

The ECU 101 controls the operation of the OCV 102 to thereby establish a communication state between the OCV 102 and the rotor side lock pin release oil passage 14, a communication state between the OCV 102 and the advance oil passage 18, and the OCV 102 and the retard oil passage 19 Switch the communication status of. The OCV 102 supplies oil supplied from an oil pump (not shown) to the rotor side lock pin releasing oil passage 14, the advance oil passage 18, or the retard oil passage 19 in accordance with the control of the ECU 101. In addition, the OCV 102 discharges the oil supplied to the rotor side lock pin releasing oil passage 14, the advance oil passage 18, or the retard oil passage 19 following a path opposite to that at the time of supply in accordance with the control of the ECU 101. .

The ECU 101 is a computer or microcomputer including a processor 101a and a memory 101b. The function of the ECU 101 is realized by software, firmware, or a combination of software and firmware. Software or firmware is described as a program and stored in the memory 101b. The processor 101a realizes the function of the ECU 101 by reading and executing a program stored in the memory 102b. That is, the ECU 101 includes a memory 102b for storing a program that, when executed by the processor 101a, results in the steps shown in the flowcharts of FIGS. It can also be said that this program causes a computer or microcomputer to execute the procedure or method shown in the flowcharts of FIGS.

Next, a control method of the valve timing adjusting device 100 by the ECU 101 will be described.
First, the unlocking procedure of the locking mechanism will be described with reference to the locking mechanism of FIGS. 14 to 17, the flowchart of FIG. 18, and the graph of FIG. In the fifth embodiment, the valve timing adjusting apparatus 100 according to the fourth embodiment is used as an example.

14 is a view showing a state in which the valve timing adjusting device 100 is locked at an intermediate position. FIG. 14A is a cross-sectional view taken along the line QQ in FIG. 3, and FIG. It is sectional drawing cut | disconnected along the P line. 15 is a view showing a state in which the advance lock pin 6 is disengaged and the retard lock pin release oil passage 5c is opened, and FIG. 15A is a cross-sectional view taken along the line QQ in FIG. FIG. 15B is a cross-sectional view taken along the line PP in FIG. 16 is a view showing a state in which the retard lock pin 7 is disengaged in addition to the advance lock pin 6, and FIG. 16A is a cross-sectional view taken along the line QQ in FIG. FIG. 4 is a cross-sectional view taken along the line PP in FIG. 3. FIG. 17 is a view showing a state in which the rotor 1 operates to the retard angle side upon receiving the retard oil pressure, FIG. 17A is a cross-sectional view taken along the line QQ in FIG. 3, and FIG. 17B is a diagram in FIG. FIG. 6 is a cross-sectional view taken along line PP.

FIG. 18 is a flowchart showing the unlocking procedure of the valve timing adjusting apparatus 100 according to the fifth embodiment. FIG. 19 is a graph showing the phase control duty, the actual phase, the release oil passage supply / discharge state, the engagement state of the advance lock pin 6, and the engagement state of the retard lock pin 7 when the lock release is performed in the fifth embodiment. It is. The phase control duty is a value for controlling the current of the OCV 102, and the hydraulic pressure in the advance hydraulic chamber 16 and the retard hydraulic chamber 17 is controlled by the ECU 101 adjusting the phase control duty. The actual phase is a relative rotation angle of the camshaft 20 with respect to the crankshaft obtained from a detection value of an angle sensor or the like. The release oil passage supply / discharge state is a value indicating the state of oil supplied / discharged from the OCV 102 to the rotor side lock pin release oil passage 14, and the larger the value, the more oil supplied to the rotor side lock pin release oil passage 14 The amount increases. The release oil passage supply / discharge state is controlled by the ECU 101. The engagement state includes the positional relationship of the advance lock pin 6 that operates in accordance with the release oil passage supply / discharge state, and the positional relationship of the retard lock pin 7 with respect to the retard engagement groove 10. Show. Engagement is a state in which the lock pin has advanced into the engagement groove and is completely fitted, and release is a state in which the lock pin has retreated from the engagement groove and has completely come out.

In a state where the rotor 1 is locked at an intermediate position, that is, as shown in FIGS. 14A and 14B, the advance lock pin 6 and the retard lock pin 7 are engaged with the advance engagement groove 9 and the retard engagement groove 10, respectively. When the engine is started while the vehicle is running, a lock release request is notified from the vehicle side to the ECU 101.

In step ST1, when the unlocking request is received from the vehicle side (step ST1 “YES”), the ECU 101 proceeds to step ST2, and otherwise (step ST1 “NO”), repeats step ST1.

In step ST2, the ECU 101 performs lock pin release control. Specifically, the ECU 101 controls the OCV 102 so as to supply the lock pin release hydraulic pressure to the rotor side lock pin release oil passage 14. The lock pin release hydraulic pressure is supplied to the advance engagement groove 9 via the rotor side lock pin release oil passage 14, the advance lock pin release oil passage 5a, and the notch 5b. Then, as shown in FIG. 15A, the lock pin releasing hydraulic pressure supplied to the advance angle engaging groove 9 acts on the advance angle lock pin 6, and the advance angle lock pin 6 is disengaged from the advance angle engagement groove 9. Is done. Further, as shown in FIG. 15B, a gap is formed between the advance lock pin 6 and the advance engagement groove 9, the retard lock pin release oil passage 5c is opened, and the lock pin release hydraulic pressure is advanced. It is supplied from the joint groove 9 to the retard lock pin releasing oil passage 5c.

In step ST3, the ECU 101 starts timing from the time when the lock pin release control is performed, and determines whether or not a predetermined set time has elapsed. If the set time has elapsed (step ST3 “YES”), the ECU 101 proceeds to step ST4, and if the set time has not elapsed (step ST3 “NO”), repeats step ST3. The set time is the time required for the lock pin release hydraulic pressure to be supplied to the rotor side lock pin release oil passage 14 and the advance angle lock pin 6 to be disengaged from the advance angle engagement groove 9, and in the graph of FIG. This corresponds to the time from lock pin release control to advance angle operation control. Note that the ECU 101 may appropriately adjust a predetermined set time according to the hydraulic pressure, the oil temperature, and the like.

In step ST4, the ECU 101 performs advance operation control. Specifically, the ECU 101 controls the OCV 102 so as to supply hydraulic pressure to the advance oil passage 18. This hydraulic pressure is supplied to the advance hydraulic chamber 16 via the advance oil passage 18. As described above, the retard lock pin 7 receives cam torque and is pressed against the retard side wall of the retard engagement groove 10 and is not easily removed. When the rotor 1 moves to the advance side as shown in FIG. 16A by the advance operation control, the retard lock pin 7 is separated from the side wall of the retard engagement groove 10 to eliminate the catch of both, and the retard lock pin 7 is in a state in which engagement can be released. Then, as shown in FIG. 16B, the lock pin releasing hydraulic pressure supplied from the retard lock pin releasing oil passage 5c to the retard engaging groove 10 acts on the retard lock pin 7, and the retard lock pin 7 is retarded. The engagement is released from the corner engagement groove 10.

The advance lock pin 6 and the retard lock pin 7 are disengaged by the control of the steps ST1 to ST4 by the ECU 101, and the intermediate lock of the rotor 1 is released. Thereafter, the ECU 101 controls the OCV 102 to supply the hydraulic pressure to the advance hydraulic chamber 16 or the retard hydraulic chamber 17 so that the target actual phase is obtained, and operates the rotor 1 to the advance side or the retard side.

Next, the locking procedure of the locking mechanism will be described with reference to the locking mechanism of FIGS. 20 to 22, the flowchart of FIG. 23, and the graph of FIG.

FIG. 20 is a view showing a state in which the rotor 1 is on the advance side, and is a cross-sectional view taken along the line QQ in FIG. 21 is a view showing a state in which the retard lock pin 7 is engaged with the stepped portion 10b of the retard engagement groove 10, and is a cross-sectional view taken along the line QQ in FIG. 22 is a view showing a state in which the valve timing adjusting device 100 is locked at the intermediate position, and is a cross-sectional view taken along the line QQ in FIG.

FIG. 23 is a flowchart showing a locking procedure of the valve timing adjusting apparatus 100 according to the fifth embodiment. FIG. 24 is a graph showing the phase control duty, the actual phase, the release oil passage supply / discharge state, the engagement state of the advance lock pin 6 and the engagement state of the retard lock pin 7 at the time of locking in the fifth embodiment. is there.

When the engagement of the advance lock pin 6 and the retard lock pin 7 is released and the engine stops in a state where the rotor 1 can be operated to the advance side and the retard side, a lock request is notified from the vehicle side to the ECU 101. Is done.

In step ST11, the ECU 101 proceeds to step ST12 when receiving a lock request from the vehicle side (step ST11 “YES”), and repeats step ST11 otherwise (step ST11 “NO”).

In step ST12, the ECU 101 controls the OCV 102 so as to supply the lock pin releasing oil pressure to the rotor side lock pin releasing oil passage 14, and supplies the lock pin releasing oil pressure to the advance angle engaging groove 9 and the retard angle engaging groove 10. . This prevents the advance lock pin 6 and the retard lock pin 7 from erroneously engaging with the advance engagement groove 9 and the retard engagement groove 10 during the advance operation of the rotor 1 in the subsequent step ST13. .

In step ST13, the ECU 101 performs advance angle operation control. Specifically, the ECU 101 supplies hydraulic pressure to the advance hydraulic chamber 16 via the advance oil passage 18 and discharges the hydraulic pressure in the retard hydraulic chamber 17 via the retard oil passage 19. Thus, the OCV 102 is controlled to move the rotor 1 to the most advanced position.

In step ST14, the ECU 101 determines whether or not the actual phase has reached the most advanced position as shown in FIG. If the actual phase is the most advanced position (step ST14 “YES”), the ECU 101 proceeds to step ST15. If the actual phase is not the most advanced position (step ST14 “NO”), step ST14 is repeated.

In step ST15, the ECU 101 performs retarded angle operation control. Specifically, the ECU 101 supplies the hydraulic pressure to the retard hydraulic chamber 17 via the retard oil passage 19 and discharges the hydraulic pressure in the advance hydraulic chamber 16 via the advance oil passage 18. The OCV 102 is controlled. Thereby, as shown in FIG. 21, the rotor 1 moves to the retard side.

In step ST16, the ECU 101 discharges the lock pin release hydraulic pressure of the advance engagement groove 9 and the retard engagement groove 10 through the rotor side lock pin release oil passage 14 simultaneously with the retard operation control of step ST15. The OCV 102 is controlled. As a result, the rotor 1 moves toward the retard side, and as shown in FIG. 21, the retard lock pin 7 is first engaged with the step portion 10 b and then is engaged with the retard engagement groove 10. . The retard lock pin 7 abuts against the retard side wall of the retard engagement groove 10 to restrict the retard operation beyond the intermediate position of the rotor 1, and the advance lock pin 6 is also an advance engagement groove. 9 is engaged. As a result, the rotor 1 is locked at the intermediate position as shown in FIG.

In step ST17, the ECU 101 determines whether or not the actual phase is stopped at the intermediate position. When the actual phase is the intermediate position (step ST17 “YES”), the ECU 101 engages the advance lock pin 6 with the advance engagement groove 9 and the retard lock pin 7 retards as shown in FIG. It is determined that the rotor 1 is locked at the intermediate position by engaging with the engaging groove 10, and the operation shown in the flowchart of FIG. On the other hand, if the actual phase is not the intermediate position (step ST17 “NO”), the ECU 101 proceeds to step ST18. When the actual phase is not at the intermediate position, the advance lock pin 6 and the retard lock pin 7 are not engaged with the advance engagement groove 9 and the retard engagement groove 10.

In step ST18, the ECU 101 determines whether or not the actual phase is retarded from the intermediate position. When the actual phase is on the retard side with respect to the intermediate position, the advance lock pin 6 and the retard lock pin 7 advance before the lock pin release hydraulic pressure is completely discharged from the advance engagement groove 9 and the retard engagement groove 10. It is considered that the engagement could not be performed because the angular engagement groove 9 and the retarded engagement groove 10 were passed, or the lock pin releasing hydraulic pressure had been discharged but the engagement failed. Therefore, when the actual phase is on the retard side with respect to the intermediate position (step ST18 “YES”), the ECU 101 returns to step ST12 and again executes the lock control routine. On the other hand, when the actual phase is not retarded from the intermediate position, it is considered that the advance lock pin 6 and the retard lock pin 7 have not yet reached the advance engagement groove 9 and the retard engagement groove 10. Therefore, when the actual phase is not retarded from the intermediate position (step ST18 “NO”), the ECU 101 returns to step ST17.

As described above, when the intermediate lock of the rotor 1 is released in the fifth embodiment, the ECU 101 supplies the lock pin release hydraulic pressure to the advance lock pin release oil passage 5a to advance the advance lock from the advance engagement groove 9. The pin 6 is disengaged to make the case 2 rotatable to the advance side, and communicated with the retard lock pin release oil passage 5 c between the advance lock pin 6 and the advance engagement groove 9. Create a gap. Next, the ECU 101 supplies hydraulic pressure to the advance hydraulic chamber 16 to rotate the rotor 1, and causes the lock pin release hydraulic pressure of the advance engagement groove 9 to pass through the clearance and the retard lock pin release oil passage 5 c. The retard lock pin 7 is supplied to the retard engagement groove 10 to release the engagement. As a result, the ECU 101 can shorten the time required to release the intermediate lock and operate the valve timing adjusting device 100 as compared with the prior art, and can improve the responsiveness.

Further, when the rotor 1 is intermediately locked in the fifth embodiment, the ECU 101 supplies the lock pin release hydraulic pressure to the advance angle engagement groove 9 and the retard angle engagement groove 10 and supplies the oil pressure to the advance angle hydraulic chamber 16. The rotor 1 is rotated to the most advanced position. Next, the ECU 101 discharges the lock pin releasing hydraulic pressure from the advance angle engaging groove 9 and the retard angle engaging groove 10, supplies the oil pressure to the retard angle hydraulic chamber 17, and rotates the rotor 1 in the direction of the intermediate position. The advance lock pin 6 is engaged with the advance engagement groove 9, and the retard lock pin 7 is engaged with the retard engagement groove 10. Accordingly, the ECU 101 automatically moves the advance lock pin 6 and the retard lock pin 7 to the advance engagement groove 9 and the retard engagement groove by operating the rotor 1 from the most advanced position to the retard side. 10 can be engaged.

Embodiment 6 FIG.
Since the valve timing adjustment device 100 according to the sixth embodiment has the same configuration as the valve timing adjustment device 100 according to the first to fourth embodiments except for the lock mechanism, FIG. 1 to FIG. 12 are used. FIG. 25 is an exploded perspective view showing a configuration example of the rotor 1 and the press-fitting member 5 in the valve timing adjustment device 100 according to the sixth embodiment. FIG. 26 is a cross-sectional view of the lock mechanism of the sixth embodiment, taken along line PP in FIG. 3, and shows a locked state.

In the first to fourth embodiments, the press-fitting member 5 is configured to have the advance lock pin release oil passage 5a. However, in the sixth embodiment, the through hole 13 is configured to have the advance lock pin release oil passage 13a. is there. As shown in FIGS. 25 and 26, a groove extending from the rotor side lock pin releasing oil passage 14 to the cutout portion 5 b of the press-fitting member 5 is formed on the inner peripheral surface of the through-hole 13. It becomes the advance lock pin release oil passage 13a.
Similarly, although the press-fitting member 5 has a configuration having the retard lock pin release oil passage 5c, the through hole 13 may have a configuration having the retard lock pin release oil passage 13b. As shown in FIGS. 25 and 26, a groove extending from the advance engagement groove 9 to the retard engagement groove 10 is formed on the inner peripheral surface of the through hole 13, and this groove is the retard lock. It becomes the pin release oil passage 13b.

In the sixth embodiment, since the vertical groove having a simple shape formed on the inner peripheral surface of the through-hole 13 is used as the advance lock pin release oil passage 13a and the retard lock pin release oil passage 13b, There is no need to process a lock pin release oil passage with a complicated shape.

In the above description, the “first” side, which is the upstream side where the lock pin release hydraulic pressure is supplied first, is the advance angle, and the “second” side, which is the downstream side, is the retard angle. Therefore, the “first lock pin” corresponds to the advance lock pin 6, and the “second lock pin” corresponds to the retard lock pin 7. The “first engagement groove” corresponds to the advance engagement groove 9, and the “second engagement groove” corresponds to the retard engagement groove 10. Furthermore, the “first lock pin release oil passage” corresponds to the advance lock pin

release oil passages

5a and 13a, and the “second lock pin release oil passage” corresponds to the retard lock pin

release oil passages

5c and 13b.

However, depending on the direction in which the valve timing adjusting device 100 is attached to the engine, the advance angle and the retard angle are reversed. That is, the advance lock pin 6 and the advance engagement groove 9 function as a retard lock pin and the retard engagement groove, and the retard lock pin 7 and the retard engagement groove 10 are the advance lock pin and the advance engagement groove. Functions as a groove. The advance lock pin

release oil passages

5a and 13a function as retard lock pin release oil passages, and the retard lock pin

release oil passages

5c and 13b function as advance lock pin release oil passages. In this case, the retard side is “first” and the advance side is “second”. Then, the advance lock pin 6 that functions as a retard lock pin is first disengaged, and then the retard lock pin 7 that functions as an advance lock pin is disengaged. It should be noted that the advance lock pin 6 that functions as a retard lock pin is difficult to come off upon receiving cam torque. Thus, the coil spring 8 having a non-linear spring constant or the two

coil springs

8a and 8b are used to weaken the force for urging the advance lock pin 6 that functions as a retard lock pin and function as an advance lock pin. It is desirable that the advance lock pin 6 functioning as the retard lock pin is surely disengaged first by increasing the force that urges the retard lock pin 7 to be engaged.

When the advance angle and the retard angle are opposite, the ECU 101 performs the retard angle operation control in step ST4 of the flowchart shown in FIG. Further, the ECU 101 performs the retard operation control in step ST13 of the flowchart shown in FIG. 23, determines whether or not the actual phase is the most retarded position in step ST15, and performs the advance operation control in step ST15. In step ST18, it is determined whether or not the actual phase is on the advance side from the intermediate position.

In the present invention, within the scope of the invention, free combinations of the respective embodiments, modification of arbitrary components of the respective embodiments, or omission of arbitrary components of the respective embodiments are possible.

Since the control device of the valve timing adjusting device according to the present invention is configured to lock the rotor at the intermediate position by the two lock pins, the control device of the valve timing adjusting device for adjusting the opening / closing timing of the intake valve and the exhaust valve of the engine Suitable for use in etc.

1 rotor (second rotating body), 2 case (first rotating body), 2a sprocket, 3 plate (first rotating body), 4 cover (first rotating body), 5 press-fitting member (cylindrical member), 5a, 13a Advance lock pin release oil passage (first lock pin release oil passage), 5b, 5c1, 5c2 Notch, 5c, 13b Delay lock pin release oil passage (second lock pin release oil passage), 5d, 5e Fluid release Path, 5f stopper, 6 advance lock pin (first lock pin), 7 retard lock pin (second lock pin), 8, 8a, 8b coil spring (biasing member), 9 advance engagement groove (first 1 engaging groove), 9a, 10a concave portion, 9b, 10b stepped portion, 10 retarded engaging groove (second engaging groove), 11 shoe, 12 vane, 13 through hole, 14 rotor side lock pin release oil passage, 15 rotor Fluid release passage, 16 advance hydraulic chamber, 17 retard hydraulic chamber, 18 advance oil passage, 19 retard oil passage, 20 camshaft, 100 valve timing adjustment device, 101 ECU (control device), 101a processor, 101b memory , 102 OCV.

Claims

A first rotating body having an operating hydraulic chamber;
A second rotating body that is housed in the first rotating body and has a vane that divides the working hydraulic chamber into an advance side and a retard side, and rotates relative to the first rotating body;
A lock mechanism for locking the second rotating body at an intermediate position between the most advanced angle position and the most retarded angle position;
The locking mechanism is
A through hole formed in the axial direction of the second rotating body in the vane;
A cylindrical cylindrical member incorporated in the through hole in a state in which axial sliding and radial rotation with the through hole are restricted;
A first lock pin and a second lock pin disposed coaxially within the cylindrical member;
A first engagement groove and a second engagement groove formed on the first rotating body and engaged with the first lock pin and the second lock pin;
A biasing member that biases the first lock pin in the direction of the first engagement groove and biases the second lock pin in the direction of the second engagement groove;
A first lock pin release oil passage formed on an outer peripheral surface of the cylindrical member or an inner peripheral surface of the through hole, and supplying a lock pin release hydraulic pressure to the first engagement groove;
A second lock pin releasing oil passage that is formed on the outer peripheral surface of the cylindrical member or the inner peripheral surface of the through hole and supplies the lock pin releasing oil pressure supplied to the first engaging groove to the second engaging groove. A control device for a valve timing adjustment device comprising:
In a state where the first lock pin is engaged with the first engagement groove and the second lock pin is engaged with the second engagement groove to lock the second rotating body at the intermediate position, The lock pin release hydraulic pressure is supplied to one lock pin release oil passage to disengage the first lock pin from the first engagement groove, and the second rotating body can be rotated to the advance side or the retard side. And a gap communicating with the second lock pin releasing oil passage is formed between the first engagement groove and the first lock pin, and the second rotating body is in a rotatable state. The hydraulic pressure chamber is supplied with hydraulic pressure to rotate the second rotating body, and the lock pin release hydraulic pressure of the first engagement groove is transferred to the second engagement via the gap and the second lock pin release oil passage. The second lock pin is disengaged by supplying to the mating groove to lock the second rotating body. Control device for a valve timing control apparatus characterized by releasing the.
When locking the second rotating body at the intermediate position,
The lock pin releasing hydraulic pressure is supplied to the first engaging groove and the second engaging groove, and the hydraulic pressure chamber is supplied to either the advance angle side or the retard angle side to supply the second rotating body. Is rotated to either the most advanced position or the most retarded position, the lock pin releasing hydraulic pressure is discharged from the first engagement groove and the second engagement groove, and either the advance side or the retard side is discharged. The hydraulic pressure is supplied to the other working hydraulic chamber to rotate the second rotating body in the intermediate position, so that the first lock pin is engaged with the first engagement groove, and the second lock pin is The control device for a valve timing adjusting device according to claim 1, wherein the second rotating body is locked by being engaged with the second engagement groove.
A first rotating body having an operating hydraulic chamber;
A second rotating body that is housed in the first rotating body and has a vane that divides the working hydraulic chamber into an advance side and a retard side, and rotates relative to the first rotating body;
A lock mechanism for locking the second rotating body at an intermediate position between the most advanced angle position and the most retarded angle position;
The locking mechanism is
A through hole formed in the axial direction of the second rotating body in the vane;
A cylindrical cylindrical member incorporated in the through hole in a state in which axial sliding and radial rotation with the through hole are restricted;
A first lock pin and a second lock pin disposed coaxially within the cylindrical member;
A first engagement groove and a second engagement groove formed on the first rotating body and engaged with the first lock pin and the second lock pin;
A biasing member that biases the first lock pin in the direction of the first engagement groove and biases the second lock pin in the direction of the second engagement groove;
A first lock pin release oil passage formed on an outer peripheral surface of the cylindrical member or an inner peripheral surface of the through hole, and supplying a lock pin release hydraulic pressure to the first engagement groove;
A second lock pin releasing oil passage that is formed on the outer peripheral surface of the cylindrical member or the inner peripheral surface of the through hole and supplies the lock pin releasing oil pressure supplied to the first engaging groove to the second engaging groove. A control method of a valve timing adjustment device comprising:
In a state where the first lock pin is engaged with the first engagement groove and the second lock pin is engaged with the second engagement groove to lock the second rotating body at the intermediate position, The lock pin release hydraulic pressure is supplied to one lock pin release oil passage to disengage the first lock pin from the first engagement groove, and the second rotating body can be rotated to the advance side or the retard side. And a gap communicating with the second lock pin releasing oil passage is formed between the first engagement groove and the first lock pin, and the second rotating body is in a rotatable state. The hydraulic pressure chamber is supplied with hydraulic pressure to rotate the second rotating body, and the lock pin release hydraulic pressure of the first engagement groove is transferred to the second engagement via the gap and the second lock pin release oil passage. The second lock pin is disengaged by supplying to the mating groove to lock the second rotating body. The method of the valve timing adjusting apparatus characterized by releasing the.
When locking the second rotating body at the intermediate position,
The lock pin releasing hydraulic pressure is supplied to the first engaging groove and the second engaging groove, and the hydraulic pressure chamber is supplied to either the advance angle side or the retard angle side to supply the second rotating body. Is rotated to either the most advanced position or the most retarded position, the lock pin releasing hydraulic pressure is discharged from the first engagement groove and the second engagement groove, and either the advance side or the retard side is discharged. The hydraulic pressure is supplied to the other working hydraulic chamber to rotate the second rotating body in the intermediate position, so that the first lock pin is engaged with the first engagement groove, and the second lock pin is The valve timing adjusting device control method according to claim 3, wherein the second rotating body is locked by being engaged with the second engaging groove.